JP2016084911A - Bearing device for wheel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device for a wheel which is improved in durability by suppressing the wear of a seal, and elongated in a life of a bearing.SOLUTION: A seal 27 is constituted of a pack seal composed of an annular seal plate 21 and a slinger 22, the seal plate 21 is composed of a core grid 23 which is pressure-inserted into an end part internal periphery of an outer ring 9, and a seal member 24 having a dust lip 24a to which a grease lip 24b and a gutter spring 25 are attached, and a side lip 24c which extends to the inside of a radial direction from a nose part of the core grid 23 while being inclined. The slinger 22 is composed of a cylinder part 22a which is pressure-inserted into an outside diameter of an inner ring 10, and an erecting plate 22b which extends to the outside of the radial disc from the cylinder part. The side lip 24c is slidably contacts with a side face of the erecting plate part via an axial fastening margin, and a labyrinth seal 26 is constituted by making an outside edge of the erecting plate 22b and an outer ring 9 oppose each other via a radial gap. A rubber magnet 28 is integrally joined to the side face of the erecting plate 22b with a vulcanization adhesive.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a full-floating type wheel bearing device that rotatably supports a drive wheel of a vehicle such as a truck with a double-row rolling bearing, and more particularly to improve wear resistance by suppressing wear of a seal. The present invention relates to a wheel bearing device with a long life.

  Many automobiles having a frame-structured body such as a truck adopt a conventional full floating type as an axle structure of a drive wheel. Also, recent drive wheel support structures are often adopted as a structure in which double row rolling bearings are unitized for the purpose of improving assemblability and reducing weight and size. As an example of the conventional structure, a wheel bearing device as shown in FIG. 8 is known.

  In this wheel bearing device, a drive shaft 52 connected to a differential (not shown) is inserted into an axle tube 51, and a double row tapered roller bearing 53 is mounted on the outer diameter surface of the axle tube 51. . A hub wheel 54 rotatably supported by the double row tapered roller bearing 53 is connected to a flange 56 of the drive shaft 52 via a hub bolt 55. A pair of left and right inner rings 57 of the double-row tapered roller bearing 53 are coupled by a connecting ring 58 and are fitted on the end of the axle tube 51 and are fastened and fixed by a fixing nut 59. The outer ring 60 of the double-row tapered roller bearing 53 is fitted into the hub ring 54 and is fixed in the axial direction with both ends thereof being sandwiched between the flange 56 and the brake rotor 61. In the annular space between the inner and outer rings 57 and 60, double-row tapered rollers 62 are rotatably accommodated by a cage 63, and seals 64 and 65 are mounted at both ends. The seal 65 prevents the lubricating grease sealed inside the bearing from leaking to the outside and prevents rainwater, dust, etc. from entering the bearing from the outside.

  In the case of this type of full floating type axle structure, the differential oil flows through the axle tube 51 and flows to the bearing outer side. Therefore, an oil seal is used as the seal 64 on the outer side of the double row tapered roller bearing 53 in contact with the differential oil. The seal 64 is mounted in a double row tapered roller bearing 53, and as shown in FIG. 9A, a cored bar 66 press-fitted into the inner periphery of the end of the outer ring 60, and the cored bar 66 by vulcanization adhesion. It is comprised by the integral type seal | sticker which consists of the sealing member 67 joined integrally.

  The seal member 67 is made of a synthetic rubber such as ACM (polyacrylic rubber) or NBR (acrylonitrile-butadiene rubber), and is formed in a bifurcated shape. The dust strip 67a is in sliding contact with the outer diameter of the inner ring 57 via a predetermined radial shimiro. And a grease lip 67b. A garter spring 68 is mounted on the outer periphery of the dust lip 67a in order to secure a stable tight force of the lip and improve the sealing performance.

  Further, a filter seal 69 is attached to the bearing 64 on the outer side of the bearing. The filter seal 69 includes a synthetic rubber mounting portion 69a in an annular seal groove 70 formed on the inner periphery of the end portion of the outer ring 60, and a filter member 69b fixed in a state of being sandwiched by the mounting portion 69a. The inner edge of the filter member 69 b is in sliding contact with the outer diameter of the inner ring 57.

  The filter member 69b is formed in a disk shape with a uniform thickness by intertwining polyester fibers, and has a function of passing differential oil but preventing contamination. As a result, the slidable contact portions of the dust lip 67a and the grease lip 67b of the seal 64 are lubricated by the differential oil that has passed through the filter member 69b, so that wear of these lips is prevented and contamination contained in the differential oil passes through the seal 64. Thus, it is possible to prevent the tapered roller 62 from being caught between the outer ring 60 and the inner ring 57, the cleanliness of the differential oil is increased, the durability and reliability of the seal 64 are improved, and the life of the bearing is extended. Can be planned.

  Further, as shown in (b), a slit 71 formed of an annular groove is formed on the inner peripheral surface of the dust strip 67a of the seal 64. The slit 71 can positively supply differential oil to the sliding contact portion of the dust lip 67a by capillary action, thereby preventing lip wear and improving the durability of the seal 64. (For example, refer to Patent Document 1).

JP 2011-69421 A

  However, the seal 64 of such a conventional wheel bearing device prevents the contamination contained in the differential oil from passing through the seal 64 by the filter member 69 b and engages between the tapered roller 62 and the outer ring 60 and the inner ring 57. However, the lip of the seal 64 is not completely sealed, and depending on the amount of the differential oil, the filter member 69b cannot prevent the entry of the contamination, and the contamination enters the dust lip 67a. There is a problem that the filter seal 69 cannot be replaced because the filter seal 69 is mounted in the bearing.

  The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a wheel bearing device in which wear of a seal is suppressed to improve durability and extend the life of the bearing. To do.

  In order to achieve such an object, the invention according to claim 1 of the present invention includes a hub wheel integrally having a wheel mounting flange for mounting a wheel, an axle tube inserted through a drive shaft, and an axle tube of the axle tube. A wheel bearing device including a wheel bearing including a double-row rolling bearing that is fitted to an outer diameter and rotatably supports the hub wheel, the wheel bearing being double-row on the inner periphery. An outer race formed integrally with the outer raceway, a pair of inner races formed with an inner raceway facing the outer raceway of the double row on the outer periphery, and both raceways of the inner race and the outer race In a wheel bearing device, comprising: a double row of rolling elements housed in a freely rotatable manner between the outer ring and a pair of inner rings; and seals attached to both side openings of an annular space formed between the outer ring and the pair of inner rings. The seal on the outer side of the seal is on the inner periphery of the outer end of the outer ring. And a seal member having a duster and a grease lip formed in a bifurcated shape integrally joined to the core by vulcanization adhesion, and the inner ring side is formed into a disk by pressing from a steel plate A sliding member having a standing plate portion formed on the core metal, and a side lip is formed integrally with the nose portion of the core metal so as to be inclined in a radial direction, and the side lip is slidably contacted with the sliding member. ing.

  As described above, a hub wheel integrally having a wheel mounting flange for mounting a wheel, an axle tube inserted through the drive shaft, and a compound wheel that is inserted into the outer diameter of the axle tube and rotatably supports the hub wheel. A wheel bearing device comprising a row of rolling bearings, the wheel bearing comprising: an outer ring integrally formed with a double row outer rolling surface on the inner periphery; A pair of inner races formed with an inner raceway facing the outer raceway surface of the row, a double row of rolling elements accommodated between the raceway surfaces of the inner race and the outer race, and a pair of outer races And a seal mounted on both side openings of an annular space formed between the inner ring of the outer ring and the outer seal of the seal is press-fitted into the inner periphery of the outer end of the outer ring. And a bifurcated joint that is integrally joined to the core by vulcanization adhesion A sliding member having a formed dust strip and a seal member having a grease lip and having a standing plate portion formed into a disk shape by pressing from a steel plate is provided on the inner ring side, and a side of the nose portion of the core metal Since the lip is integrally formed with a slant in the radial direction, and the side lip is slidably contacted with the sliding member, it is possible to prevent the diff oil from entering the bearing and preventing contamination from reaching the dust lip. It is possible to provide a wheel bearing device in which the wear of a seal is suppressed to improve durability and to extend the life of the bearing.

  Preferably, as in the second aspect of the invention, if a magnet is joined to the side surface of the upright plate portion of the sliding member, metal contamination is adsorbed and diff oil enters the bearing to cause contamination. Can prevent dust from reaching the dust lip, and in the market, it is possible to clean the contaminants adsorbed on the magnet or replace the magnet itself, thereby improving the durability by suppressing the wear of the seal over a long period of time. Can be made.

  Further, as in the invention according to claim 3, the outer side seal is constituted by a pack seal formed of an annular seal plate and a slinger that are formed in an L shape in cross section and arranged to face each other, The seal plate is composed of the core metal and the seal member, the slinger is composed of the sliding member, and a cylindrical portion that is press-fitted into the outer diameter of the inner ring, and a vertical plate portion that extends radially outward from the cylindrical portion. The labyrinth seal may be configured such that the outer edge of the upright plate portion faces the inner periphery of the end portion of the outer ring via a radial clearance.

  According to a fourth aspect of the present invention, the outer-side seal is formed of a pack seal including an annular seal plate and a slinger that are formed in an L shape in cross section and arranged to face each other. The seal plate is composed of the core metal and the seal member, the slinger is composed of the sliding member, and a cylindrical portion that is press-fitted into the outer diameter of the inner ring, and a vertical plate portion that extends radially outward from the cylindrical portion. A cylindrical sliding contact portion bent to the inner side from the outer edge of the upright plate portion, and protruding radially outward from the sliding contact portion so as to face the seal plate via a radial clearance. If the side lip is slidably in contact with the sliding contact portion of the slinger via a radial shimoshiro, a lip oil can be further prevented from entering the seal, and the side lip can be further prevented. Is worn The foil is also trying to penetrate into the seal, the labyrinth structure between the sliding portion and the flange portion of the seal member and the slinger can be prevented from entering the sealing internal contamination.

  In addition, as in the fifth aspect of the present invention, if the annular space formed between the seal plate and the slinger is previously filled with clean differential oil, the differential oil is always supplied to the sliding contact portion of the dust lip. The wear of the dust lip can be prevented and the durability of the seal can be further improved.

  According to a sixth aspect of the present invention, the side lip is curved from the nose portion of the core bar and extends in a radially outward direction, and is slidably contacted with the sliding member via an axial shimiro. If this is done, it is possible to further prevent the differential oil from entering the seal, and to prevent the side lip of the seal member from expanding due to the centrifugal force associated with the rotation and increasing the axial swaying with the sliding member. It is possible to prevent an increase in sliding resistance and suppress heat generation and lip wear.

  Further, as in the invention described in claim 7, if the inner ring is fixed to the end of the axle tube by a fixing nut via a washer, and the sliding member is constituted by the washer, By joining the magnet, metal contamination is adsorbed, and the diff oil can enter the inside of the bearing and prevent the contamination from reaching the dust lip. In addition, the contamination adsorbed by the washer in the market is removed from the magnet or washer. It can be easily replaced.

  A wheel bearing device according to the present invention includes a hub wheel integrally having a wheel mounting flange for mounting a wheel, an axle tube inserted through a drive shaft, and an outer diameter of the axle tube. A wheel bearing device comprising a double row rolling bearing that rotatably supports a wheel bearing device, wherein the wheel bearing has a double row outer rolling surface formed integrally on the inner periphery. An outer ring, a pair of inner rings each having an inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a plurality of inner rings and a plurality of inner rings that are accommodated in a freely rolling manner between the inner and outer rolling surfaces. In a wheel bearing device comprising: a rolling element in a row; and seals mounted on both side openings of an annular space formed between the outer ring and the pair of inner rings, the outer seal of the seals , A core bar press-fitted into the inner periphery of the outer end of the outer ring, and the core And a seal member having a duster lip and a grease lip formed integrally with each other by vulcanization adhesion, and a slide having a standing plate portion formed into a disc shape by pressing from a steel plate on the inner ring side. A moving member is provided, and a side lip is integrally formed at the nose portion of the core metal so as to be inclined in the radial direction. The side lip is slidably contacted with the sliding member, so that differential oil enters the bearing. Thus, it is possible to provide a wheel bearing device that can prevent contamination from reaching the dust lip, suppress wear of the seal, improve durability, and extend the life of the bearing.

It is a longitudinal section showing one embodiment of a wheel bearing device concerning the present invention. It is a longitudinal cross-sectional view which shows the wheel bearing of FIG. It is a principal part enlarged view which shows one seal | sticker of FIG. It is a principal part enlarged view which shows the modification of the seal | sticker of FIG. It is a principal part enlarged view which shows the modification of the seal | sticker of FIG. It is a principal part enlarged view which shows the other modification of the seal | sticker of FIG. It is a principal part enlarged view which shows the other modification of the seal | sticker of FIG. It is a longitudinal cross-sectional view which shows the conventional wheel bearing apparatus. (A) is an enlarged view showing one seal unit of FIG. 8, (b) is an arrow view seen from the IX direction of the seal of (a).

  A hub wheel integrally having a wheel mounting flange for mounting a wheel, an axle tube inserted through a drive shaft, and a double row that is inserted into an outer diameter step portion of the axle tube and rotatably supports the hub wheel. A wheel bearing device comprising a rolling bearing comprising: an outer ring having a double row outer rolling surface integrally formed on an inner periphery; and A pair of inner rings formed with an inner rolling surface facing the outer rolling surface of the row, a double row tapered roller housed in a freely rolling manner between the rolling surfaces of the inner ring and the outer ring, and the outer ring And a seal mounted on both side openings of the annular space formed between the inner ring and the pair of inner rings, wherein the outer seal of the seals has an L-shaped cross section And a seal composed of an annular seal plate and a slinger arranged opposite to each other. Consists of a seal, and the seal plate is formed by press-fitting into the inner periphery of the end of the outer ring, and vulcanized and bonded integrally to the core, and extending in a forked manner from the inner diameter of the core A duster lip having a grease lip and a garter spring, and a side lip extending inwardly in a radial direction from a nose portion of the metal core, and a cylindrical portion into which the slinger is press-fitted into the outer diameter of the inner ring; The vertical lip portion extends radially outward from the cylindrical portion, and the side lip is slidably contacted to the inner side surface of the vertical plate portion via an axial shimiro, and the outer edge of the vertical plate portion is A labyrinth seal is configured to face the inner periphery of the end portion of the outer ring via a radial clearance, and a rubber magnet is integrally joined to the outer side surface of the upright plate portion by vulcanization adhesion.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention, FIG. 2 is a longitudinal sectional view showing a wheel bearing of FIG. 1, and FIG. 3 shows one seal of FIG. FIG. 4 is an enlarged view of an essential part showing a modified example of the seal of FIG. 3, FIG. 5 is an enlarged view of an essential part showing a modified example of the seal of FIG. 4, and FIG. The principal part enlarged view which shows another modification, FIG. 7 is a principal part enlarged view which shows the other modification of the seal | sticker of FIG. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).

  In this wheel bearing device, a drive shaft 2 connected to a differential (not shown) is inserted into an axle tube 1, and a wheel bearing 3 is mounted on the outer diameter surface of the axle tube 1. The hub wheel 4 is rotatably supported by the wheel bearing 3. The hub wheel 4 is connected to the flange 6 of the drive shaft 2 via a hub bolt 5. The wheel bearing 3 is fitted into the hub wheel 4, and both ends thereof are sandwiched between the flange 6 and the brake rotor 7, and a pair of inner rings 10 and 10, which will be described later, are attached to the outer end of the axle tube 1. It is externally fitted and fastened and fixed by a fixing nut 8.

  As shown in an enlarged view in FIG. 2, the wheel bearing 3 is an outer ring (outer member) in which tapered double-row outer rolling surfaces 9 a and 9 a that are outwardly opened on the inner circumference are integrally formed. 9 and a pair of inner races 10, 10 each having a tapered inner rolling surface 10a facing the double row outer rolling surfaces 9a, 9a on the outer periphery, and a cage 11 between both rolling surfaces. And two rows of rolling elements (conical rollers) 12 and 12 accommodated so as to be freely rollable. A large collar portion 10b for guiding the rolling element 12 is formed on the large diameter side of the inner raceway surface 10a of the inner ring 10, and a small collar portion 10c for preventing the rolling element 12 from dropping off on the small diameter side. Are integrally formed. The pair of inner rings 10, 10 is set in a state where the end surfaces on the side of the small flange 10 c are abutted to each other, thereby constituting a back-to-back type wheel bearing 3.

  Annular grooves 13 and 13 are formed at the inner peripheral ends on the small diameter side of the pair of inner rings 10 and 10, and a connecting ring 14 is attached to these annular grooves 13 and 13. The connecting ring 14 is formed into a generally ring-shaped ring shape by pressing a steel plate such as tool steel or spring steel, and is generally formed into a ring shape having an end, and the surface is tempered or quenched to a range of 40 to 55 HRC. A curing process is applied.

  The outer ring 9 and the inner ring 10 are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC to the core part by quenching. On the other hand, the rolling elements 12 are formed of high carbon chrome steel such as SUJ2 as in the outer ring 9 and the inner ring 10, and are hardened in the range of 62 to 67HRC to the core part by quenching.

  Seals 15 and 16 are attached to openings on both sides of an annular space formed between the outer ring 9 and the pair of inner rings 10 and 10, and the inner side seal 15 is connected to the outside of the lubricating grease sealed in the bearing. The outer seal 16 prevents the diff oil from entering the inside of the bearing. In addition, although the double row tapered roller bearing which used the tapered roller for the rolling element 12 was illustrated as the wheel bearing 3 here, it is comprised not only in this but the double row angular ball bearing which uses the ball for the rolling element. Also good.

  Here, the seal 15 on the inner side constitutes a so-called pack seal composed of an annular seal plate 17 and a slinger 18 which are formed in a substantially L-shaped cross section and are arranged to face each other. The seal plate 17 includes a cored bar 19 that is press-fitted into the inner periphery of the end of the outer ring 9, and a seal member 20 that is integrally vulcanized and bonded to the cored bar 19 and has a plurality of lips.

  As shown in an enlarged view in FIG. 3, the outer-side seal 16 constitutes a pack seal composed of an annular seal plate 21 and a slinger 22 that are substantially L-shaped in cross section and arranged to face each other. . The seal plate 21 includes a core metal 23 press-fitted into the inner periphery of the end of the outer ring 9 and a seal member 24 integrally joined to the core metal 23 by vulcanization adhesion.

  The core 23 is made of a ferritic stainless steel plate (JIS standard SUS430 series, etc.), an austenitic stainless steel plate (JIS standard SUS304 series, etc.), or a rust-proof cold-rolled steel plate (JIS standard SPCC system, etc.). A cylindrical fitting portion 23a having a substantially L-shaped cross section by press working and press-fitted into the inner periphery of the outer side end portion of the outer ring 9 via a predetermined shimoshiro, and an end portion of the fitting portion 23a And an inner diameter portion 23b extending radially inward. And the nose part (tip part) of the fitting part 23a is formed thinner than the other part, and the sealing member 24 wraps around and joins from the inner diameter part 23b so as to cover the tip part, so-called half metal structure. I am doing. Thereby, the airtightness of the fitting part 23a can be improved and the inside of a bearing can be protected.

  On the other hand, the seal member 24 is made of synthetic rubber such as ACM or NBR, and is fitted with a dust lip 24a, a grease lip 24b, and a cored bar 23, which are formed to extend from the end of the inner diameter part 23b of the cored bar 23. A side lip 24c is provided extending obliquely inward in the radial direction from the nose portion of the portion 23a. A garter spring 25 is attached to the outer periphery of the dust lip 24a in order to ensure a stable tight force of the lip and improve the sealing performance. In addition to the ACM and NBR exemplified as the material of the seal member 24, for example, HNBR (hydrogenated acrylonitrile butadiene rubber), EPDM (ethylene propylene rubber), etc. having excellent heat resistance, heat resistance, Examples thereof include FKM (fluorine rubber) or silicon rubber having excellent chemical properties.

  The slinger 22 is formed of a ferritic stainless steel plate, an austenitic stainless steel plate, or a cold-rolled steel plate that has been rust-proofed and formed into a substantially L-shaped section by press working, and is a cylinder that is press-fitted into the outer diameter of the inner ring 10. It consists of a portion 22a and a standing plate portion 22b extending radially outward from the cylindrical portion 22a. The dust strip 24a and the grease lip 24b of the seal member 24 are slidably contacted with the cylindrical portion 22a via a predetermined radial shimiro, and the side lip 24c is slid with respect to the upright plate portion 22b via a predetermined axial shimillo. It is touched. In the slinger 22, the surface roughness of the steel plate as the material is set in the range of Ra 0.2 to 0.6. Thereby, a favorable seal sliding contact surface can be obtained, and lip wear can be suppressed. Note that Ra is one of JIS roughness shape parameters (JIS B0601-1994), and is an arithmetic average roughness, which means an average value of absolute value deviations from an average line.

  Further, the outer edge of the standing plate portion 22b of the slinger 22 is opposed to the inner periphery of the end portion of the outer ring 9 with a slight radial clearance δ to constitute a labyrinth seal 26. The clearance δ of the labyrinth seal 26 is such that the slinger 22 and the outer ring 9 do not come into contact with each other due to dimensional variations in manufacturing of the slinger 22 including the coaxiality of the inner and outer rings 10 and 9, and a desired sealing property is secured. Therefore, the range of 0.25 mm ≦ δ ≦ 0.75 mm on one side (radius) is preferable.

  As described above, in the present embodiment, the outer seal 16 is constituted by a pack seal having the slinger 22, and the outer edge of the standing plate portion 22 b of the slinger 22 has a slight radial clearance from the inner periphery of the end of the outer ring 9. The labyrinth seal 26 is configured to face each other, and the seal member 24 has a side lip 24c, and the side lip 24c is slidably contacted with the standing plate portion 22b of the slinger 22, so that the differential oil enters the bearing. Thus, it is possible to provide a wheel bearing device that can prevent contamination from reaching the dust strip 24a, suppress wear of the seal, improve durability, and extend the life of the bearing.

  The seal 27 shown in FIG. 4 is a modification of FIG. 3 and basically differs only in part of the configuration of the seal 16 described above, and the same reference numerals are given to other parts and parts having the same function or the same function. A detailed description thereof will be omitted.

  This seal 27 constitutes a pack seal comprising an annular seal plate 21 and a slinger 22 which are formed in a substantially L-shaped cross section and are arranged to face each other. The seal plate 21 includes a core metal 23 press-fitted into the inner periphery of the end of the outer ring 9 and a seal member 24 integrally joined to the core metal 23 by vulcanization adhesion.

  In the present embodiment, the slinger 22 is a cylinder that is formed into a substantially L-shaped section by pressing from a ferritic stainless steel plate or a cold-rolled steel plate that has been rust-proofed, and is press-fitted into the outer diameter of the inner ring 10. The magnet 22 is integrally joined to the outer side surface of the standing plate 22b by vulcanization bonding or the like. The portion 22a is a vertical plate 22b extending radially outward from the cylindrical portion 22a. The magnet 28 is a rubber magnet in which an elastomer such as rubber is mixed with magnetic powder such as ferrite. In this example, the magnet 28 is made of a rubber magnet. However, the present invention is not limited to this. For example, the magnet 28 may be formed of a sintered alloy, or may be a plastic magnet joined.

  This magnet 28 attracts metal contamination and prevents the diff oil from entering the inside of the bearing to prevent the contamination from reaching the dust lip 24a, and it is possible to clean the contamination adsorbed on the slinger 22 in the market. Thus, it is possible to improve the durability by suppressing the wear of the seal 27 over a long period of time.

  Further, by filling the annular space formed between the seal plate 21 and the slinger 22 with clean differential oil in advance, the differential oil can be constantly supplied to the sliding contact portion of the dust strip 24a. Thus, the durability of the seal 27 can be further improved.

  The seal 29 shown in FIG. 5 is a modification of FIG. 4 and basically differs only in the configuration of the seal 27 and the slinger 22 described above. The same reference numerals are given to the same parts or parts having the same function. A detailed description thereof will be omitted.

  In this seal 29, the side lip 24c of the seal member 24 is in sliding contact with the washer 30 instead of the slinger 22 of the seal 27 described above. Specifically, the seal 29 includes an annular seal plate 21 composed of a core metal 23 press-fitted into the inner periphery of the end of the outer ring 9 and a seal member 24 integrally joined to the core metal 23 by vulcanization adhesion. I have. The seal member 24 constituting the seal plate 21 is made of synthetic rubber such as ACM or NBR, is formed to extend from the end of the inner diameter portion 23b of the core metal 23, and is slidably contacted with the outer diameter surface of the inner ring 10. A strip 24a, a grease lip 24b, and a side lip 24c extending obliquely inward in the radial direction from the tip end of the fitting portion 23a of the metal core 23 are provided.

  Here, the inner ring 10 is externally fitted to an outer end of an axle tube (not shown), and is fastened and fixed by a fixing nut 8 via a washer 30 formed into a disk shape by pressing from a steel plate. The outer diameter of the washer 30 is extended, and the outer edge of the washer 30 is opposed to the inner periphery of the end of the outer ring 9 with a slight radial clearance δ to constitute the labyrinth seal 26. The magnet 28 is integrally joined to the outer side surface of the washer 30 by the magnetic force, and the side lip 24c of the seal member 24 is slidably contacted to the inner side surface of the washer 30 via a predetermined axial squeeze. ing.

  As in the above-described embodiment, this makes it possible to prevent metal contamination from being attracted by the magnet 28 and prevent the diff oil from entering the bearing and reaching the dust lip 24a. The adsorbed contamination can be removed from the magnet 28 or the washer 30 itself can be easily replaced.

  The seal 31 shown in FIG. 6 is another modification of FIG. 4 and basically differs in the configuration of the seal 27 and the slinger 22 described above, but is the same for other parts and parts having the same parts or the same functions. Reference numerals are assigned and detailed description thereof is omitted.

  The seal 31 constitutes a pack seal composed of an annular seal plate 21 and a slinger 32 which are formed in a substantially L-shaped cross section and arranged to face each other. The seal plate 21 includes a core metal 23 press-fitted into the inner periphery of the end of the outer ring 9 and a seal member 24 integrally joined to the core metal 23 by vulcanization adhesion.

  On the other hand, the slinger 32 is formed into a substantially L-shaped section by pressing from a ferritic stainless steel plate, an austenitic stainless steel plate, or a cold-rolled steel plate that has been rust-proofed, and is press-fitted into the outer diameter of the inner ring 10. A cylindrical portion 22a, a standing plate portion 22b extending radially outward from the cylindrical portion 22a, a cylindrical sliding contact portion 32a bent from the outer edge of the standing plate portion 22b to the inner side, and the sliding contact The flange 32b protrudes radially outward from the portion 32a and is opposed to the seal plate 21 via a radial clearance to form a labyrinth seal. The dust lip 24a and the grease lip 24b of the seal member 24 are slidably contacted with the cylindrical portion 22a via a predetermined radial shimiro, and the side lip 24c is slid with respect to the sliding contact portion 32a via a predetermined radial shimillo. It is touched. As a result, even if the side lip 24 c is worn and the differential oil is about to enter the seal 31, the labyrinth structure between the seal member 24, the sliding contact portion 32 a of the slinger 32, and the flange portion 32 b causes the contamination to enter the seal 32. Can be prevented.

  In the present embodiment, the magnet 28 is integrally joined to the inner side surface of the standing plate portion 22 b of the slinger 32. Thereby, since the magnet 28 is not exposed to the outside, it is possible to prevent a defect such as a defect by interfering with peripheral parts at the time of assembly process or parts replacement in the market.

  Next, another modification of the seal 16 of FIG. 3 is shown in FIG. Basically, the seal 33 is different only in the configuration of the seal plate 21 of the seal 16 described above, and other parts and parts having the same parts or parts having the same functions are denoted by the same reference numerals and will be described in detail. Omitted.

  The seal 33 constitutes a pack seal composed of an annular seal plate 34 and a slinger 22 which are substantially L-shaped in cross section and arranged to face each other. The seal plate 34 includes a cored bar 23 press-fitted into the inner periphery of the end of the outer ring 9, and a seal member 35 integrally joined to the cored bar 23 by vulcanization adhesion.

  The sealing member 35 is made of a synthetic rubber such as ACM or NBR, and has a dust lip 24a and a grease lip 24b formed extending from the end of the inner diameter portion 23b of the core metal 23 and a fitting portion 23a of the core metal 23. The side lip 35a is provided that is curved from the tip of the lip and extends in a radially outward direction.

  In this embodiment, the side lip 35a of the seal member 35 is inclined and extended outward in the radial direction, so that the lip oil can be further prevented from entering the seal by increasing the lip inclination angle and rotating. An increase in torque can be prevented. That is, in this type of wheel bearing, since the outer ring 9 rotates, it is possible to prevent the side lip 35a of the seal member 35 from expanding due to the centrifugal force associated with the rotation and increasing the axial swaying with the slinger 22. It is possible to prevent an increase in sliding resistance and suppress heat generation and lip wear.

  The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

  The wheel bearing device according to the present invention can be applied to a full floating type wheel bearing device on the side of a driving wheel in which wheel bearings are mounted in openings of a driving shaft and an axle tube.

DESCRIPTION OF SYMBOLS 1 Axle tube 1a Shoulder part 2 Drive shaft 3 Wheel bearing 4 Hub wheel 5 Hub bolt 6 Flange 7 Brake rotor 8 Fixing nut 9 Outer member 9a Outer rolling surface 10 Inner ring 10a Inner rolling surface 10b Large collar part 10c Small collar part DESCRIPTION OF SYMBOLS 11 Cage 12 Rolling body 13 Annular groove 14 Linking ring 15 Inner side seal 16, 27, 29, 31, 33 Outer side seal 17, 21, 34 Seal plate 18, 22, 32 Slinger 19, 23 Core metal 20, 24, 35 Seal members 22, 32 Slinger 22a Cylindrical portion 22b Standing plate portion 23a Fitting portion 23b Inner diameter portion 24a Dustrip 24b Grease lip 24c, 35a Side lip 25 Garter spring 26 Labyrinth seal 28 Magnet 30 Washer 32a Sliding contact portion 32b Part 51 Axle tube 52 Drive shaft 53 Double row tapered roller bearing 54 Hub wheel 55 Hub 56 Nuts 56 Flange 57 Inner ring 58 Connecting ring 59 Fixing nut 60 Outer ring 61 Brake rotor 62 Tapered roller 63 Cage 64, 65 Seal 66 Core metal 67 Seal member 67a Dustrip 67b Grease lip 68 Garter spring 69 Filter seal 69a Mounting part 69b Filter member 70 Seal groove 71 Slit δ Radial clearance of labyrinth seal

Claims (7)

A hub wheel integrally having a wheel mounting flange for mounting the wheel;
An axle tube inserted through the drive shaft;
A wheel bearing device including a wheel bearing formed of a double row rolling bearing that is fitted to the outer diameter of the axle tube and rotatably supports the hub wheel,
This wheel bearing has an outer ring in which a double row outer rolling surface is integrally formed on the inner periphery,
A pair of inner rings formed on the outer periphery with an inner rolling surface facing the double row outer rolling surface;
A double row rolling element housed in a freely rolling manner between the rolling surfaces of the inner ring and the outer ring,
In a wheel bearing device comprising: seals mounted on both side openings of an annular space formed between the outer ring and a pair of inner rings,
Of the seals, an outer side seal is a core metal press-fitted into the inner periphery of the outer side end of the outer ring, and a duster and a green formed in a bifurcated shape integrally joined to the core metal by vulcanization adhesion. A seal member having a slip;
A sliding member having a standing plate portion formed into a disk shape by pressing from a steel plate is provided on the inner ring side, and a side lip is integrally formed in the nose portion of the core metal in a radial direction, The wheel bearing device according to claim 1, wherein the side lip is in sliding contact with the sliding member.   The wheel bearing device according to claim 1, wherein a magnet is joined to a side surface of the standing plate portion of the sliding member.   The outer side seal is composed of a pack seal made up of an annular seal plate and a slinger that are formed in an L-shaped cross section and arranged to face each other, and the seal plate is made up of the core metal and the seal member The slinger includes the sliding member, and includes a cylindrical portion that is press-fitted into the outer diameter of the inner ring, and a vertical plate portion that extends radially outward from the cylindrical portion, and an outer edge of the vertical plate portion is connected to the outer ring. 2. The wheel bearing device according to claim 1, wherein a labyrinth seal is configured to face the inner periphery of the end portion through a radial clearance.   The outer side seal is composed of a pack seal made up of an annular seal plate and a slinger that are formed in an L-shaped cross section and arranged to face each other, and the seal plate is made up of the core metal and the seal member The slinger is composed of the sliding member, and is a cylindrical portion that is press-fitted into the outer diameter of the inner ring, a standing plate portion that extends radially outward from the cylindrical portion, and is folded from the outer edge of the standing plate portion to the inner side. A curved cylindrical sliding contact portion, and a collar portion that protrudes radially outward from the sliding contact portion and is opposed to the seal plate via a radial clearance to form a labyrinth seal, and the side lip The wheel bearing device according to claim 1, wherein the sliding contact portion of the slinger is slidably contacted with each other via a radial shimiro.   The wheel bearing device according to claim 3 or 4, wherein a clean differential oil is previously filled in an annular space formed between the seal plate and the slinger.   2. The wheel bearing device according to claim 1, wherein the side lip is curved from the nose portion of the cored bar and extends in a radially outward direction, and is slidably contacted with the sliding member via an axial nip. .   The wheel bearing device according to claim 1, wherein the inner ring is fixed to an end portion of the axle tube by a fixing nut via a washer, and the sliding member is configured by the washer.

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